JPS5942812B2 - flat force meter - Google Patents
flat force meterInfo
- Publication number
- JPS5942812B2 JPS5942812B2 JP53077115A JP7711578A JPS5942812B2 JP S5942812 B2 JPS5942812 B2 JP S5942812B2 JP 53077115 A JP53077115 A JP 53077115A JP 7711578 A JP7711578 A JP 7711578A JP S5942812 B2 JPS5942812 B2 JP S5942812B2
- Authority
- JP
- Japan
- Prior art keywords
- load cell
- disc
- disc spring
- transmitting member
- force transmitting
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L1/00—Measuring force or stress, in general
- G01L1/20—Measuring force or stress, in general by measuring variations in ohmic resistance of solid materials or of electrically-conductive fluids; by making use of electrokinetic cells, i.e. liquid-containing cells wherein an electrical potential is produced or varied upon the application of stress
- G01L1/22—Measuring force or stress, in general by measuring variations in ohmic resistance of solid materials or of electrically-conductive fluids; by making use of electrokinetic cells, i.e. liquid-containing cells wherein an electrical potential is produced or varied upon the application of stress using resistance strain gauges
- G01L1/2206—Special supports with preselected places to mount the resistance strain gauges; Mounting of supports
- G01L1/2231—Special supports with preselected places to mount the resistance strain gauges; Mounting of supports the supports being disc- or ring-shaped, adapted for measuring a force along a single direction
Description
【発明の詳細な説明】
本発明は、厚さが半径方向で変化しており、補強された
外側端縁領域を有する軸対称の第１円板ばねと、この第
１円板はねＧこ荷重力を加える為の中央受圧部とを具え
るロードセルであって、前記の第１円板ばねの一方の而
は主として平坦となっており、他方の面は脆弱領域を形
成する形状となっており、この脆弱領域の区域内に１個
以上の歪計が設けられているロードセルＱこ関するもの
である。DETAILED DESCRIPTION OF THE INVENTION The present invention provides an axisymmetric first disc spring having a radially varying thickness and a reinforced outer edge region; A load cell comprising a central pressure-receiving part for applying a load force, wherein one surface of the first disc spring is mainly flat, and the other surface is shaped to form a weakened region. This relates to a load cell Q in which one or more strain gauges are provided within the area of this weakened region.
上述した種類のロードセルは英国特許第
９２２９８２号明細書ζこ記載されており、この場合、
円板ばねの外側の端縁領域を下方に厚肉（こしてこの端
縁領域を剛固Ｏこ補強してあり、円板ばねの下面Ｏこ歪
計が装着されており、互い（こ１２０°ずらした３つの
ボルトＯこより端縁領域の下部（こ蓋が取付けられてお
り、これらのボルトが脚部としである表面上Ｏこ配置さ
れること（こよりロードセルが支持されるようＱこなも
ている。A load cell of the type described above is described in British Patent No. 922,982, in which case:
The outer edge area of the disk spring is reinforced with a thick wall (thick wall) downward, and a strain gauge is attached to the lower surface of the disk spring. The three staggered bolts should be placed at the bottom of the edge area so that the lid is attached and these bolts are placed on the surface of the leg so that the load cell is supported. I have it.
剛固な端縁領域は、円板ばねの中央の受圧部Ｑこ加わる
加重が変化する際に前記のボルトとこれらが配置される
前記の表面との間に生じる相対移動およびこれＱこよっ
て生じる摩擦損失を制限する作用をする。The rigid edge area is caused by the relative movement that occurs between the bolts and the surface on which they are arranged when the load applied to the central pressure receiving part Q of the disc spring changes and this occurs. It acts to limit friction losses.
しかし、円板ばねの端縁領域すなわちボルトの半径方向
のこの移動は、外側の端縁領域を極めて厚肉Ｑこしても
完全には除去されない。However, this movement in the radial direction of the edge region of the disk spring, i.e. of the bolt, is not completely eliminated even with a very thick wall Q in the outer edge region.
本発明の目的は上述した種類の既知のロードセルに摺動
摩擦によって生じる摩擦損失を最小とすることＯこある
。It is an object of the invention to minimize the frictional losses caused by sliding friction in known load cells of the type mentioned above.
本発明は、厚さが半径方向で変化しており、補強された
外側端縁領域を有する軸対称の第１円板はねと、この第
１円板はねに荷重力を加える為の中央受圧部とを具える
ロードセルであって、前記の第１円板ばねの一方の面は
主として平坦となっており、他方の面は脆弱領域を形成
する形状となっており、この脆弱領域の区域内Ｏこ１個
以上の歪計が設けられているロードセルＱこおいて、前
記第１円板はねと同様Ｏこ構成した第２円板ばねをこの
第１円板はねと同心的に配置し、これら２つの円板はね
の主として平坦な面を互いに対向させ、これら２つの円
板ばねの補強端縁領域間ζこ配置した環状の力伝達部材
Ｏこよりこれら円板ばねを離間関係に保持し、前記の歪
計はこれら円板はねのいずれか一方に取付けたことを特
徴とする。The present invention comprises an axisymmetric first disk slat having a radially varying thickness and a reinforced outer edge area, and a central portion for applying a loading force to the first disk slat. One surface of the first disk spring is mainly flat, and the other surface is shaped to form a fragile region, and the region of the fragile region is A load cell Q is provided with one or more strain gauges, and a second disc spring having an O-shape configuration similar to the first disc spring is placed concentrically with the first disc spring. The two disc springs are arranged so that the mainly flat surfaces of these two disc springs face each other, and the annular force transmitting member O is arranged between the reinforcing edge regions of these two disc springs so that these disc springs are spaced apart from each other. It is characterized in that the strain gauge is attached to either one of these disc springs.
本発明Ｏこよれば、荷重状態において、力伝達部材に当
接する２つの円板ばねの平坦面の半径方向の移動中、こ
れらの２つの平坦間には相対的な半径方向移動は生ぜず
、またこれと同時の力伝達部材の半径方向の伸張或いは
収縮中円板ばねがこの力伝達部材上をころがる。According to the present invention, during the radial movement of the flat surfaces of the two disc springs that abut the force transmitting member in the loaded state, no relative radial movement occurs between these two flat surfaces; Also, during the simultaneous radial extension or contraction of the force transmitting member, the disk spring rolls on this force transmitting member.
その理由は、荷重を受けた一方の円板ばねが下方に凸と
なるように彎曲し、他方の円板ばねが上方に凸となるよ
うに彎曲する為である。The reason for this is that one of the disk springs subjected to the load bends downwardly to convex, and the other disk spring bends upwardly.
従って円板ばねと力伝達部材との間Ｏこはロッキングチ
ェアーの原理のように主としてころがり摩擦のみが生じ
、従って２つの円板はね間の力の伝達はほとんど摩擦を
生ゼしぬることなく行なわれ、ヒステリシスおよびこれ
に伴なう非直線性が減少し、正確な平型ロードセルを得
ることができる。Therefore, just like the principle of a rocking chair, only rolling friction occurs between the disk spring and the force transmitting member, and therefore the force is transmitted between the two disks with almost no friction. As a result, hysteresis and associated nonlinearity are reduced, and an accurate flat load cell can be obtained.
力伝達部材は１００〜２５０ＧＰａの弾性係数を有する
金属或は合金、例えば青銅或は黄銅から造るのが好まし
い。Preferably, the force transmitting member is made of a metal or alloy, such as bronze or brass, with a modulus of elasticity of 100 to 250 GPa.
力伝達部材は容器内をころがる球体のリングとするか、
或いは円板ばねＯこ円周的に接触する面を有する一体の
環状体とすることができる。The force transmitting member may be a spherical ring that rolls within the container, or
Alternatively, the disc spring O can be an integral annular body having circumferentially contacting surfaces.
本発明による他の例では、２つの円板ばねを、これらの
周縁上に設けられ荷重力が与えられた際にこれら円板ば
ねの端縁領域間を自由に相対移動させうる弾性外被部材
Ｏこよって互に保持する。In another embodiment according to the invention, the two disc springs are provided with an elastic jacket member which is arranged on their periphery and allows free relative movement between the edge regions of the disc springs when a loading force is applied. O holds each other together.
図面につき本発明を説明する。The invention will be explained with reference to the drawings.
図面は本発明（こよるロードセルの一例を示す断面図で
ある。The drawing is a sectional view showing an example of a load cell according to the present invention.
このロードセルは軸対称の２つの円板ばね１および２を
有し、これら円板ばね１および２はほぼ同じ幾例学的寸
法を有しこれら円板ばねのほぼ平坦な表面が互い（こ対
向するように互いに同心的Ｏこ配置する。This load cell has two axially symmetrical disk springs 1 and 2, which have approximately the same geometrical dimensions and whose substantially flat surfaces are opposite each other. Place them concentrically with each other so that
圧縮荷重の場合矢印Ｐの方向でロードセルに作用する力
が加わり、図面で見て下方に突出するスピゴット５を有
する丸型ヘッド部材８を介して所定の方向に力が加わる
よう（こする。In the case of a compressive load, a force acting on the load cell in the direction of the arrow P is applied, and a force is applied in a predetermined direction (rubbing) via a round head member 8 having a spigot 5 projecting downwards as seen in the drawing.
例えば弾性ディスク４０こ当接するこの丸型ヘッド部材
３はそのスピゴット５ｃこよって円板ばね１の孔６内（
こ移動自在（こ取付ける。For example, the round head member 3 that comes into contact with the elastic disk 40 is pushed into the hole 6 of the disc spring 1 by its spigot 5c (
This is movable (this can be installed).
２つの円板ばね１および２間には、これらの補強した外
側端縁部２１および２２の領域において、環状の力伝達
部材７を心合せして配置する。Between the two disk springs 1 and 2, in the region of their reinforced outer edges 21 and 22, an annular force transmission element 7 is arranged aligned.
例えばこの力伝達部材７が、円板ばねの２つの対向する
面の各々に１つずつ設けた環状の案内溝（図示せず）内
に位置するようにするか、或はこの力伝達部材７にスペ
ーサを設け、これらスペーサを、円板はね１および２の
周縁上Ｏこ設けられこれら円板ばねを互いＯこ保持する
ようなこする外被部材８まで到達せしめるようにする。For example, the force transmitting member 7 may be located in annular guide grooves (not shown) provided one on each of the two opposite sides of the disc spring; spacers are provided in such a way that they reach up to a rubbing jacket member 8 which is provided on the periphery of the disk springs 1 and 2 and which holds the disk springs together.
外被部材８は２つの円板はね１および２の全周縁に亘っ
て設けた溝９に掛合させる。The outer cover member 8 is engaged in a groove 9 provided over the entire circumference of the two disk springs 1 and 2.
外被部材８は例えば合成材料或は薄肉金属板のような弾
性材料から造り、ロードセルが荷重された際に生じる円
板は４忌１および２の外側端縁部２１および２２の移動
が妨害されないようにする。The outer cover member 8 is made of an elastic material, such as a synthetic material or a thin metal plate, so that the movement of the outer edge portions 21 and 22 of the outer edges 1 and 2 of the disk formed when the load cell is loaded is not obstructed. Do it like this.
前述した半径方向の所望な伸張変化を得る為に、２つの
円板ばね１および２の外側の面（互い（こ対向しない面
）を、脆弱な領域が得られる形状にし、また大部分が平
坦なこれらの円板ばねの対向面が、最大の伸張（荷重を
加えた際）或は圧縮（荷重を除去した際）が生じる脆弱
領域で例えば蒸着した或は箔の歪計１０を収容するよう
にする。In order to obtain the desired radial extension change mentioned above, the outer surfaces of the two disk springs 1 and 2 (the surfaces that do not face each other) are shaped to provide a weak area and are mostly flat. The opposing faces of these disk springs are arranged to accommodate strain gauges 10, e.g. vapor-deposited or foil, in the weakened region where maximum extension (on application of load) or compression (on removal of load) occurs. Make it.
本例では、４つの歪計１０を円板はね２の平坦上に配置
し、これら歪計の電気接続用リード線（図示せず）を溝
１１および孔１２を経て導出させる。In this example, four strain gauges 10 are arranged on the flat surface of the disc spring 2, and lead wires (not shown) for electrical connection of these strain gauges are led out through grooves 11 and holes 12.
円板ばね１のボス１３は過荷重保護部材として作用し、
荷重限界を越えた際Ｏこ２つの円板はわが互いＯこ直接
当接するようにする。The boss 13 of the disc spring 1 acts as an overload protection member,
When the load limit is exceeded, the two discs will come into direct contact with each other.
ロードセルを支持体（図示せず）上（こ装着する為（こ
、荷重を支持体に伝達する力出力部材をも構成する軸１
４を設ける。In order to mount the load cell on a support (not shown), the shaft 1 also constitutes a force output member that transmits the load to the support.
4 will be provided.
力伝達部材７は例えば容器内Ｏこ入れた多数の球体とす
ることができ、これらの球体は１００〜２５０ＧＰａの
弾性係数を有する金属或は合金、好適ζこは青銅或は黄
銅から造る。The force transmitting member 7 can be, for example, a number of spheres placed inside the container, these spheres being made of a metal or alloy, preferably bronze or brass, having a modulus of elasticity of 100 to 250 GPa.
外側端縁部２１および２２の対向面は硬化させた。Opposing surfaces of outer edges 21 and 22 were hardened.
他の側の力伝達部材７は、円板ばね１および２の各々に
円周的（こ当接する面を有しまた円形成は長円或いは二
重凸状の断面を有する例えば青銅或は黄銅のリングとす
る。The force transmitting member 7 on the other side is made of bronze or brass, for example, and has a surface that contacts each of the disc springs 1 and 2 in a circumferential manner, and the circular shape has an oval or double convex cross section. The ring shall be
また、このリングは三角形成は四角形等の多角形の断面
を有するようにすることができ、そのとがった端縁を２
つの円板ばね１および２に円周的０こ当接させることが
できる。In addition, this ring can have a triangular shape or a polygonal cross section such as a quadrilateral, and its pointed edges can be
The two disc springs 1 and 2 can be brought into contact with each other at zero circumference.
従ってこの種のリングは、２つの互い（こ対向する環状
の刃型軸受によって支承される。This type of ring is therefore supported by two mutually opposing annular blade bearings.
圧力ＰをロードセルＯこ及ぼすと、円板ばね１が下方（
こ凸状となり、円板ばね２が上方（こ凸状となる。When pressure P is applied to load cell O, disc spring 1 moves downward (
It has a convex shape, and the disc spring 2 is upward (has a convex shape).
従って２つの円板ばねがリング７上をころがり同時Ｏこ
このリング７がリングの半径方向で外方（こ伸張され、
従って摩擦損失がころがり摩擦によるほんのわずかの摩
擦損失のみとなる。Therefore, the two disk springs roll on the ring 7 and at the same time the ring 7 is stretched outward in the radial direction of the ring.
Therefore, the friction loss is only a small amount due to rolling friction.
図面は本発明によるロードセルの一例を示す断面図であ
る
１、２・・・・・・円板ばね、８・・・・・・元型ヘッ
ド部材、４・・・・・・弾性ディスク、５・・・・・・
スピゴット、６・・・・・・孔、７・・・・・・力伝達
部材、８・・・・・・外被部材、９・・・・・・溝、１
０・・・・・・歪計、１１・・・・・・溝、１２・・・
・・・孔、１３・・・・・・ボス、１４・・・・・・軸
、２１，２２・・・・・・外側端縁部。The drawing is a cross-sectional view showing an example of a load cell according to the present invention.・・・・・・
Spigot, 6... Hole, 7... Force transmission member, 8... Covering member, 9... Groove, 1
0...Strain meter, 11...Groove, 12...
... Hole, 13 ... Boss, 14 ... Shaft, 21, 22 ... Outer edge.
Claims (1)
縁領域を有する軸対称の第１円板はねと、この第１円板
ばねに荷重力を加える為の中央受圧部とを具えるロード
セルであって、前記の第１円板ばねの一方の面は主とし
て平坦となっており、他方の面は脆弱領域を形成する形
状となっており、この脆弱領域の区域内（こ１個以上の
歪計が設けられているロードセルにおいて、前記第１円
板ばねと同様に構成した第２円板ばねをこの第Ｉ円板ば
ねと同心的に配置し、これら２つの円板ばねの主として
平坦な面を互いＯこ対向させ、これら２つの円板ばねの
補強端縁領域間に配置した環状の力伝達部材Ｏこよりこ
れら円板ばねを離間関係Ｏこ保持し、前記の歪計はこれ
ら円板ばねのいずれか一方（こ取付けたことを特徴とす
るロードセル。 ２、特許請求の範囲１記載のロードセルにおいて、前記
の力伝達部材を１００〜２５０ＧＰａ 弾性係数を有す
る金属或は合金から違ったことを特徴とするロードセル
。 ３ 特許請求の範囲１記載のロードセル０こおいて、前
記力伝達部材を青銅或は黄銅から造ったことを特徴とす
るロードセル。 ４ 特許請求の範囲１ないし３のいずれか１っＱこ記載
のロードセル（こおいて、前記の力伝達部材は容器内を
ころがる球体のリングを有することを特徴とするロード
セル。 ５ 特許請求の範囲１ないし３のいずれか１つに記載の
ロードセル（こおいて、前記の力伝達部材を、前記の円
板ばねの各々ｔこ円周的に線接触する形状としたリング
としたことを特徴とするロードセル。 ６ 特許請求の範囲１ないし５のいずれか１っＱこ記載
のロードセルにおいて、前記の２つの円板ばねをこれら
の周縁上σこ設けた弾性外被部材ｌこよって互いに保持
したことを特徴とするロードセルClaims: 1. An axially symmetrical first disc spring of varying thickness in the radial direction and having a reinforced outer edge area and for applying a loading force to this first disc spring. A load cell comprising a central pressure receiving part, wherein one surface of the first disc spring is mainly flat, and the other surface is shaped to form a weak region, and the first disk spring has a shape that forms a weak region. (In a load cell in which one or more strain gauges are provided, a second disc spring configured similarly to the first disc spring is arranged concentrically with this I-th disc spring, and these The mainly flat surfaces of the two disc springs are opposed to each other, and the disc springs are held in a spaced apart relationship by an annular force transmitting member disposed between the reinforced edge regions of the two disc springs. 2. The load cell according to claim 1, wherein the strain gauge has an elastic modulus of 100 to 250 GPa. A load cell characterized in that it is made of a metal or an alloy. 3. A load cell according to claim 1, wherein the force transmitting member is made of bronze or brass. 4. Claims Claims 1 to 3: The load cell according to claim 1, wherein the force transmitting member has a spherical ring that rolls within a container.5 Claims 1 to 3 2. The load cell according to any one of the above, wherein the force transmitting member is a ring having a shape that makes line contact with each of the disc springs circumferentially. 6. The load cell according to any one of Claims 1 to 5, characterized in that the two disc springs are held together by an elastic jacket member L provided on their peripheries. load cell
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2729064A DE2729064C2 (en) | 1977-06-28 | 1977-06-28 | Symmetrical flat load cell |
| DE000P27290648 | 1977-06-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5412875A JPS5412875A (en) | 1979-01-30 |
| JPS5942812B2 true JPS5942812B2 (en) | 1984-10-17 |
Family
ID=6012550
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP53077115A Expired JPS5942812B2 (en) | 1977-06-28 | 1978-06-27 | flat force meter |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US4146864A (en) |
| JP (1) | JPS5942812B2 (en) |
| DE (1) | DE2729064C2 (en) |
| FR (1) | FR2396278A1 (en) |
| GB (1) | GB2000597B (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3241850C2 (en) * | 1982-11-12 | 1984-08-30 | Hottinger Baldwin Messtechnik Gmbh, 6100 Darmstadt | Force measuring device |
| GB8624340D0 (en) * | 1986-10-10 | 1986-11-12 | Badcock F D M | Drum weigher |
| DE3823673A1 (en) * | 1988-07-13 | 1990-01-18 | Philips Patentverwaltung | PRINT OR Force transducer with an axial symmetrical, pressure or Force absorbing circular plate spring |
| DE4009019C2 (en) * | 1990-03-21 | 1998-07-23 | Philips Patentverwaltung | Circular plate spring for a load cell |
| DE4232785A1 (en) * | 1992-09-30 | 1994-03-31 | Philips Patentverwaltung | Circular plate spring for a load cell |
| DE9312740U1 (en) * | 1993-08-25 | 1994-10-06 | Siemens Ag | Ring bar load cell with ring notches for nominal load adjustment |
| EP1340968B1 (en) * | 2002-02-27 | 2006-10-18 | S.C.A.I.M.E. S.A. | Flexion force sensor and balance equipped with such flexion force sensors |
| US7447051B2 (en) * | 2004-10-12 | 2008-11-04 | Halliburton Energy Services, Inc. | Synchronous multi-phase AC-to-DC converter |
| EP1876136B1 (en) * | 2006-07-04 | 2012-01-11 | Herrmann Werkstatt-Technk GmbH | Supporting element |
| US7790437B2 (en) * | 2006-12-14 | 2010-09-07 | Biorep Technologies, Inc. | Organ transportation device |
| WO2014008377A1 (en) * | 2012-07-05 | 2014-01-09 | Ian Campbell | Microelectromechanical load sensor and methods of manufacturing the same |
| JP2019105469A (en) * | 2017-12-11 | 2019-06-27 | 日立オートモティブシステムズ株式会社 | Load sensor and electric brake |
| JP6872475B2 (en) * | 2017-12-26 | 2021-05-19 | ミネベアミツミ株式会社 | Multi-axis actuator with integrated load sensor and load sensor |
| WO2020102778A1 (en) * | 2018-11-15 | 2020-05-22 | Intuitive Surgical Operations, Inc. | Strain sensor with contoured deflection surface |
| MX2022002147A (en) | 2019-08-21 | 2022-05-18 | Freightlucid LLC | Bulk metallic glass load cell. |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2995034A (en) * | 1956-05-01 | 1961-08-08 | Budd Co | Load-cell devices |
| DE1022035B (en) * | 1957-04-18 | 1958-01-02 | Schenck Gmbh Carl | Force measuring device with strain gauges |
| US2992556A (en) * | 1958-04-23 | 1961-07-18 | Webster Instr Inc | Force measuring instrument |
| DE1129317B (en) * | 1960-10-14 | 1962-05-10 | Schenck Gmbh Carl | Load cell |
| DE1226806B (en) * | 1960-11-29 | 1966-10-13 | Siemens Ag | Load cell |
| US3402609A (en) * | 1964-09-29 | 1968-09-24 | Tokota Chuo Kenkyusho Kk | Semiconductor mechanical-to-electrical transducer |
| NL6414342A (en) * | 1964-12-10 | 1966-06-13 | ||
| US3439761A (en) * | 1966-10-17 | 1969-04-22 | Blh Electronics | Strain-gage transducer structures |
| FR1532022A (en) * | 1967-07-21 | 1968-07-05 | Blh Electronics | Strain gauge transducer device |
-
1977
- 1977-06-28 DE DE2729064A patent/DE2729064C2/en not_active Expired
-
1978
- 1978-06-09 US US05/914,066 patent/US4146864A/en not_active Expired - Lifetime
- 1978-06-23 GB GB7827702A patent/GB2000597B/en not_active Expired
- 1978-06-26 FR FR7818963A patent/FR2396278A1/en active Granted
- 1978-06-27 JP JP53077115A patent/JPS5942812B2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| GB2000597A (en) | 1979-01-10 |
| US4146864A (en) | 1979-03-27 |
| DE2729064A1 (en) | 1979-01-11 |
| FR2396278A1 (en) | 1979-01-26 |
| GB2000597B (en) | 1982-01-27 |
| DE2729064C2 (en) | 1985-04-11 |
| JPS5412875A (en) | 1979-01-30 |
| FR2396278B1 (en) | 1982-08-13 |
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